IMPROVED DISC CUTTER AND EXCAVATION EQUIPMENT
TECHNICAL FIELD
This invention relates to improved seals for rolling type disc cutters, useful to provide an improved disc cutter for cutting rock and hard soils, and additionally, to improved cutterheads employing such small diameter disc cutters for use with drilling, boring, tunneling machines, and other mechanical excavation equipment.
BACKGROUND
A variety of cutter or bits are known in the art of mechanical excavation. One type of cutter commonly used on large diameter cutterheads in rock excavation is the disc type rolling cutter. Disc cutters are presently frequently used on cutterheads employed in tunnel boring, raise drilling, and large diameter blind drilling.
In hard rock, the disc type cutter operates on the principle that by applying great thrust on the cutter, and consequently pressure on the rock to be cut, a zone of rock directly beneath (i.e., in the cutting direction) and adjacent to the disc cutter is crushed, normally forming very fine particles. The crushed zone forms a pressure bulb of fine rock powder which exerts a hydraulic like pressure downward (again, the cutting direction) and outward against adjacent rock. The adjacent rock then cracks, and chips spall from the rock face being excavated.
The present invention is directed to a novel disc cutter which dramatically improves production rates of disc cutter excavation, which also allows reduced thrust requirements for cutterhead penetration, which in turn reduces the weight of the structure required to support the cutters. Such reductions also allow disc cutter technology to be applied to novel, small diameter cutterheads for excavation equipment. Additionally, the relatively light weight of our disc cutters provides dramatically decreased parts and labor costs for the maintenance and replacement of cutterhead wear parts.
BRIEF DESCRIPTION OF THE DRAWING
For a better understanding of the nature, objects and advantages of our invention, the general principles of its operation, and of the prior art pertaining thereto, reference should be had to the following detailed description, taken in conjunction with the accompanying drawing, in which:
Theorv:
FIG. 1 is generalized vertical cross-sectional view illustrating the principles of rock cutting by use of rolling type disc cutters, showing in partial cross-section the exemplary disc cutter of the present invention.
FIG. 2 is a graphic illustration of the relationship between specific energy required for excavation and mean particle size.
FIG. 3 is a rock face view showing the pattern left in a rock face when an excavating device using rolling type disc cutters is employed.
FIG. 4 is a graphic illustration of the relationship between spacing ratio of rolling disc cutters and the compressive strength of the rock against which the cutter is working.
FIG. 5 is generalized graphic illustration of the relationship between the thrust force used and the rock penetration achieved during excavation, illustrating the critical force required for cutting rock, to excavate.
Prior Art:
FIG. 6 is a vertical cross-sectional view of a typical prior art large size rolling type disc cutter using tapered roller bearings.
Novel Disc Cutter:
FIG. 7 is an exploded vertical cross-sectional view of one embodiment of our rolling type disc cutter, revealing (a) a shaft, (b) wear ring, (c) seal, (d) cutter ring or blade, (e) bearing, (f) bearing retainer, and (g) hubcap, all assembled on a pedestal mount.
FIG. 7A is a cross-sectional view of a shaft for a rolling disc cutter, were a hardened washer surface is used and where such washer surface is provided as an integral part of the shaft structure.
FIG. 7B is an enlarged vertical cross-sectional view of a substantially semi-circular shaped disc cutter ring as employed in one embodiment of our novel disc cutter.
FIG. 8 is an exploded perspective view showing the assembly of one embodiment of our disc cutter assembly, showing (a) a shaft, (b) wear ring, (c) cutter blade (with bearing and seal assembled, but hidden), (d) a bearing
FIG. 9 is vertical cross-sectional view of a fully assembled disc cutter of the type first illustrated in FIGS.
7 and 8 above.
Test Apparatus:
FIG. 10 is a schematic illustrating the testing apparatus used for gathering initial performance and structural data on our novel disc cutters.
FIG. 11 is a schematic illustrating the forces acting on a disc cutter.
FIG. 12 is a schematic illustrating some of the important measurements with respect to work done on a rock face which is cut with rolling disc cutters.
Cutter Blade Details:
FIG. 13 is an axial cross-sectional view of c disc cutter utilizing a hard metal cutting blade insert, before wear on the cuttin blade insert begins via use in cutting rock.
FIG. 14 is an axial cross-sectional view of an used disc cutter utilizing a hard metal cutting blade insert, showing disc cutter shape retention via the self sharpening cutter blade described herein.
Prior Art Cutter Blade Details:
FIG. 15 shows an axial cross-sectional view of an unused prior art all metal disc cutter blade.
FIG. 16 shows an axial cross-sectional view of R used prior art all metal disc cutter blade.
FIG. 17 is a transverse view with a partial cut-away showing a cross-section of a prior art disc cutter blade which used button type hard metal inserts.
wear pattern of the button type hard metal insert found in some prior art disc cutter designs.
Hard Metal Cutter Blade Details:
FIG. 18 is a transverse cross-sectional view of our novel disc cutter design with a hard metal segmented cutting edge, using twelve hard metal inserts.
FIG. 18A is an enlarged transverse cross-sectional view of a hard metal segment as used in one embodiment of our novel disc cutter, showing three critical radii which when properly sized will achieve desired reliability of hard metal segment inserts.
FIG. 18B is an axial cross-sectional view a hard metal insert segment as used in one embodiment of our novel disc cutter, illustrating one critical radius which when properly shaped will achieve desired minimum lateral forces necessary to achieve the desired reliability of the disc cutters.
FIG. 18C is a transverse cross-sectional view of our novel disc cutter design showing a second embodiment of our hard metal segmented cutting edge design, utilizing four hard metal segments.
Further Embodiments:
FIG. 19 is an axial cross-sectional view of a second embodiment of our novel fully assembled disc cutter, shown utilizing a hard metal insert cutting edge.
FIG. 19A is a partial axial cross-sectional view of the disc cutter ring first shown in FIG. 19, now illustrating resulting structure when the hard metal inserts are brazed to the cutter ring.
FIG. 20 is a top view, looking downward on a disc cutter ring of the type set forth in FIG. 19, showing a twelve segment hard metal insert design in its ope:rating configuration.
Cutterheads (and their details):
FIG. 21 is a side perspective view, looking slightly upward, oblique to the face of a cutterhead which is designed for use of the novel disc cutters disclosed herein.
FIG. 22 is a bottom view, taken as if from the cutting face looking up directly at the cutterhead first illustrated in FIG. 21.
FIG. 23 is a vertical cross-sectional view, taken partially as if through section 23-23 of FIG. 22 but also showing a rock face being cut, to shown the cantilever mounting technique for attaching our disc cutter to a cutterhead.
FIG. 24 is a cross-sectional view of one embodiment of a cutterhead, illustrating use of a central drive shaft with drilling fluid (slurry) muck removal, and showing space allowed behind cutters to enable cuttings to escape away from the cutter face.
FIG. 25 is a cross-sectional view of another embodiment of a cutterhead using our disc cutter, shcwing a peripheral drive technique, as well as the space allowed behind cutters to enable cuttings to escape away from the cutter face.
FIG. 26 is a cross-sectional view of a shaft mounted blind drilling cutterbody which employs our novel disc cutters, and which, as illustrated, uses a pneumatic system
Core Drill Bit:
FIG. 27 is a vertical cross sectional view of a core drilling bit employing the novel disc cutters as described herein.
FIG. 28 is a bottom view, taken from the working face looking back toward the drilling bit, here looking upward at the cutting face of the core drilling bit first illustrated in FIG. 27 above.
Alternate Bearing Arrangements:
FIG. 29 is a vertical cross-sectional view of our disc cutter, showing yet another embodiment utilizing a journal type bearing.
FIG. 30 is a vertical cross-sectional view of the disc cutter of the present invention, showing our disc cutter being utilized in a saddle mounted shaft type application.
FIG. 31 is a vertical cross-sectional view of the novel disc cutter disclosed herein, showing a saddle mounted shaft type application, and employing journal bearings.
FIG. 32 is a vertical cross-sectional view of yet another embodiment of our disc cutter, illustrating the use of a full face seal and roller-ball type bearing arrangement.
FIG. 33 is an exploded vertical cross-sectional view of the embodiment of our novel rolling type disc cutter just illustrated in FIG. 32 above, revealing (a) a shaft, (b) the full face type seal, (c) the cutter ring or blade, (d) the roller-ball type bearing, (e) a bearing retainer, (f) hubcap with zerk fitting and alternate plug, and (g) retaining
FIG. 34 is a vertical cross sectional view of yet another embodiment of our novel disc cutter, similar to the embodiment just illustrated in FIGS. 32 and 33 above, and using a similar bearing and seal arrangement, but now utilizing a hard metal insert type cutting edge.
FIG. 35 is a vertical cross sectional view of still another embodiment of our novel disc cutter, sornewhat similar to the embodiment shown in FIGS. 32 and 33 above, but now utilizing a flanged cutter ring and a half-face type seal, wherein the seal is provided between the rotating, generally chevron shaped sealing ring type washer, and the interior end of the inner bearing race.
FIG. 36 is a vertical cross-sectional view, similar to FIG. 23 above, illustrating the cantilever mounting technique and also employing an alternate embodiment of our novel disc cutter in a cutterhead which utilizes a single," or one-half face seal arrangement and roller-ball bearings.
FIG. 36A is a vertical cross-sectional view of yet another embodiment of our novel disc cutter, similar to the embodiment just illustrated in FIG. 36 above, but with the disc cutter now utilizing a hard insert type cutting edge, while employing a bearing and seal arrangement as just shown in FIG. 36.
FIG. 37 is a vertical cross-sectional view of still another embodiment of our novel disc cutter, where the disc cutter now employs a inwardly facing "single" or one-half face type seal arrangement and a pair of inwardly centered angled needle bearings.
FIG. 38 is a vertical cross-sectional view of still cutter now employs an outwardly facing "single" or one-half face type seal arrangement and needle radial bearings with a combination retainer and thrust washer, where the washer takes axial load in both directions.
FIG. 39 is a vertical cross-sectional view of still another embodiment of our novel disc cutter, where the disc cutter now employs an outwardly facing "single" or one-half face type seal arrangement and a journal type radial bearing.
FIG. 40 is a vertical cross-sectional view of still another embodiment of our novel disc cutter, where the disc cutter now employs an "O-ring" seal centered in grooves provided in the cutter ring and on a portion of the shaft, and where an angled journal bearing is utilized to provide for both radial and axial loads.
FIG. 41 is a side elevation view of the hubcap used on the disc cutter illustrated in the accompanying FIG. 40.
In order to minimize repetitive description, throughout the various figures, like parts are given like reference numerals to the extent feasible.
THEORY
The fundamental operational principles involved in using a disc cutter for rock excavation are well known by those familiar with the art to which this specification is addressed. However, a review of such principles will enable the reader, regardless of whether long skilled in or now new to the art, to appreciate the significant improvement in the arrangements for our novel disc cutter designs, and which is achieved by the cutterheads using our disc cutter designs.
Attention is directed to FIG. 1, which shows a hard rock 40 being cut by disc type cutters 42 and 44. Although the cutters 42 and 44 are shown in this FIG. 1 in the design of the novel disc cutters described and claimed herein, the general principles of disc cutter operation are the same as with various heretofore known disc cutter devices; those prior art devices will in due course be distinguished from the exemplary novel cutters 42 and 44. By applying pressure downward from adjacent cutters 42 and 44 toward rock 40, a zone 46 of rock directly beneath each disc cutter is crushed. The force required to form the crush zone 46 is a function of both cutter geometry and characteristics of the rock, particularly the compressive strength of the rock.
Zones 46 provide a pressure bulb of fine rock powder which exerts a downward and outwardly extending hydraulic-like pressure into the rock 40. This pressure causes cracks 48a, 48b, 48c, 48d, etc., to form in the rock 40. When the cracks 48a and 48b contact each other, a rock chip 50 palls off the surface 52 of the rock 40. The objective of efficient rock cutting is to crush a minimum of rock 46 and spall off chips 50 which are as large as possible, thus maximizing the volume of rock chips 50 produced by the chipping action.
To form the maximum volume of large chips 50, the lateral spacing S between the kerf or path 52a and 52b of adjacent cutters (see FIG. 3) such as cutters 42 and 44 in
FIG. 1, should be maximized. In that way, a minimum amount maximum size chip 50 is produced. Generally, this concept may be expressed as a relationship between mean particle size and the specific energy required for the rock 40 being excavated. One customary unit of measure in which the specific energy requirement is often expressed is in terms of horsepower-hour required per ton of rock excavated. FIG.
2 graphically expresses this relationship between mean particle size (i.e., rock chip 50 size) and the specific energy required. As is evident from FIG. 2, it would be advantageous to increase the mean particle size, or rock chip size 50, in order to reduce the amount of energy required to excavate in a given rock 40. FIG. 2 also reveals that if a present method of excavation produces particles (chips) of small average size, performance (rock output per unit of time) can be greatly enhanced (as much as 10 times) at the same horsepower input by substantially increasing the mean particle size. As described herein below, our novel disc cutter design is able to achieve such an increase in mean particle size in certain applications, which is quite extraordinary, for example, when compared to use of certain roller cone type cutters presently used in drilling.
As illustrated in FIG. 3, when drilling in rock a rock 40, a concentric circle pattern is typically created when single rolling disc cutters such as cutters 42 and 44 are acting on the face 60 of the rock 40. Chips 50 tend to be proportional to the distance S between concentric paths or kerfs 52a, 52b, 52c, 52d, etc. which are cut by the disc cutters such as cutters 42 and 44. It is most efficient to etc. (single tracking) . In summary, a series of properly spaced disc cutters, cutting repeatedly in the same parallel or concentric kerf 52a, or 52b, or 52c, etc. (to take advantage of previously formed cracks) is the most efficient mechanical technique for cutting rock heretofore known. Our invention improves upon this technique.
Directing attention again to FIG. 1, when cutter 42 or 44 is cutting rock 40, the cutters 42 and 44 penetrate into rock 40 by a depth Y. A relationship exists between the depth of penetration Y into the rock 40 and the the spacing or width S between blades of cutters 62 and 54 of cutters 42 and 44, as shown in FIG. 4. This relationship is simply expressed as a spacing ratio, i.e., the distance between kerbs (e.g. the distance between kerf 52a and 52b) divided by the depth of penetration Y. Generally speaking, in order to increase spacing S, and thus to improve rock cutting efficiency (in terms of specific energy), a cutter must be thrust deeper (larger penetration Y) into the rock 40.
Without regard to the specific type of rolling disc cutter being used, in general, the spacing ratio will be lower in softer or more elastic rock, and can be increased in harder, more brittle rock.
Parameters which affect penetration Y are (1) characteristics of the rock being cut, (2) thrust of the cutter blade against the rock, (3) the diameter Df a selected cutter, and (4) blade width of the cutter. The latter two parameters, taken together, are frequently referred to as the cutter "footprint." Any given cutter configuration, on any given rock, must achieve a threshold for that specific rock type before significant indentation (penetration in the Y direction) of the rock will occur; this relationship is presented in FIG. 5. As thrust is initially increased, minimal penetration Y occurs. At thrust forces above the "critical force", penetration Y varies as a proportional function of the thrust force.
The critical force is a function of rock characteristics (primarily hardness, toughness, porosity, crystalline structure and microfractures) and of disc cutter blade geometry (primarily cutter diameter, blade shape and blade width). On hard rocks, with the disc type cutters known heretofore, the critical force can easily be 50,000 lbs. or more, depending upon the cutter configuration and rock characteristics.
THE PRIOR ART
As discussed above, it is generally known in the art that a relationship exists between penetration Y and spacing
S, and between increased spacing S and the production of larger rock chips, and that production of larger chips will normally result in increased efficiency (i.e., lower specific energy). The method which has heretofore been employed by others in the art to exploit this relationship has been to use larger and larger diameter disc cutters.
Such large diameter cutter designs have been adapted to accommodate high thrust forces by provision of larger and larger bearings. Such bearings have been used to allow rotation of the cutter at the increased thrust force on the rock which is necessary in order to achieve deeper
In so far as we are aware, tunnel boring machine ("TBM") manufacturers have heretofore generally employed a disc cutter configuration similar to that shown in FI-. 6.
Such disc cutters 70 are now most commonly produced and sold with a diameter D of 17 in. (43.18 cm), 18.25 in (46.36 cm), 19 in. (48.26 cm) , and 20 in. (50.8 cm). Also, such cutters 70 have been saddle mounted, that is the shaft 72 is supported at both ends (74 and 76) . This has been structurally desirable, to avoid deflection, and generally necessary in order to withstand the high thrusts required for rock penetration. Blade (cutter tip or rim) 78 widths W of 0.5 inch (1.27 cm) to 0.8 inch (2.03 cm) are most common.
The largest cutters of which we are aware have a claimed thrust capacity of up to 75,000 pounds force. That is, by way of the forces imposed on the cutterhead, and through the cutter shaft 72, and supported by a saddle type mount (not shown) on both ends 74 and 76 of the shaft 72, the cutter blade or ring 78 can in turn exert 75,000 lbs force normal to a rock face.
Although conventional disc cutter technology has thus increased the depth of cut (penetration Y) by increasing thrust capacity of the cutter, the desired increased thrust capacity has been achieved by resorting to larger and larger diameter disc cutters. This trend by others has resulted in their use of a series of large bearings, normally o: the double tapered roller type 80, which in turn require large diameter cutter rings 78 to allow space within the cutter 70 to accommodate the large bearing 80 mechanisms. For example, in a cutter 70 of seventeen (17) inches (43.18 cm) diameter together (B1+B1) range up to thirty five percent (35%) or more of the total diameter D. Thus, a high percentage of the total radial space in the design is used up as bearing space B1.
The relatively small shaft diameter A resultingly leaves the radial space occupied by the shaft 72 (or axle) insufficiently large for use in cantilever mounting of the prior art cutters 70. Therefore, such prior art cutters have normally had a shaft which is supported at both ends, or "saddle mounted."
These large size, heavy weight cutters such as cutter 70, and their accompanying saddle type shaft mounts, make modern single row, rotating disc cutters useable only in conjunction with large diameter cutterheads. Due to the size and weight of the prior art large diameter disc cutter designs, it is not practical (or even possible, in many cases) to use such disc cutters in smaller diameter cutterheads, much less in drilling bits. As a result, in so far as we are aware, rotating disc cutters have not generally been used, if used at all, in such applications.
Also, as can be appreciated from the study of the prior art cutter 70 illustrated in FIG. 6, the assembly and disassembly of such prior art cutters is complex. The cutter 70 contains over twenty (20) parts. In the most common size (seventeen (17) inches (43.18 cm) diameter) such cutters 70 are quite heavy, usually in the 350 lb. range. Major parts of prior art cutter 70 include the inner bearing races 82 and 82', tapered bearings 80 and 80', outer bearing races 86 and 86', a hub 88 with a radial flange or rib 92 on the outer shoulder 94, and a retainer ring 96. When cutters of the blade or cutter ring 78 or replacement of the bearings 80 or 80', the entire cutter assembly 70 (as shown is removed from a boring machine and carried away from the point of excavation.
Generally cutters 70 are too heavy for manual removal and carriage by workmen, and therefore must be removed with the help of lifting equipment and transported by conveyance to a cutter repair shop outside of the tunnel or excavation site, in order to be repaired or rebuilt. There, using special tools, the cutter ring 78 and possibly seals 98, 100, 102, and 104, as well as bearings 80 and 80' and their respective races when necessary (inner races 82 and 82', and outer races 86 and 86'), are replaced and the cutter assembly 70 is returned to the excavating machine. Such prior art large disc type cutters are described in various patents; U.S. Patent No. 4,784,438, issued Nov. 15, 1988 to Tyman Fikse for TUNNELING MACHINE
ROTATABLE MEMBER, is representative.
Various attempts have also been made to improve the design of disc type cutters. One attempt which superficially resembles one embodiment of our improved cutter disc is described in U.S. Patent No. 3,791,465, issued Feb. 12, 1974 to Metge for BORING TOOL. That patent describes the use of carbide or nitride plates inserted at the outer periphery of a cutter wheel to provide a continuous cutting edge, rather than using buttons.
However, although Metge tries to reduce the shock applied to a hard metal insert by using a continuous edge rather than spaced buttons to impact the rock face, he does not address the precise shape of such plates which we have found of cutter blade inserts. Nor does Metge utilize an inserted segment to provide a self sharpening cutter ring as we will describe hereinbelow. Finally, Metge does not address the problem of differential thermal expansion between the hard metal inserts and the cutter blade steel, a quite serious matter which we have solved.
Other types of drilling applications are also of interest, since in addition to use of our novel disc cutter design in boring or excavating equipment as already described, our disc cutter may be advantageously applied in relatively small diameter drilling applications.
Heretofore, for example, tri-cone type drill bits have been commonly used in drilling holes up to about twenty three (23) inches (58.42 cm) in diameter. Bits of that type commonly employ carbide button inserts, either in multi-row or randomly close spaced patterns. Drilling using such prior art tri-cone bits typically results in production of rock material ranging in particle size from powder to a coarse granular sand. The specific energy expended in using such tri-cone bits is in the range of approximately 80 horsepower-hours per ton (HP-hr/ton) and upward for excavation. However, by use of our disc cutter design in cutterheads in this size range, the specific energy required for such drilling operations can be dramatically reduced.
In summary, insofar as we are aware, no bearing and structural support configurations have heretofore been provided or suggested (1) for small diameter disc cutters (i.e. preferably in the range of about fourteen (14) inches (35.56 cm) diameter and smaller, and more preferably in the smaller, and most preferably in the five (5) inch (12.7 cm) diameter range or smaller) with the structural capability to reliably endure the high thrusts required to meet and exceed the critical pressure required for rock excavation, cr (2) are of a size which can advantageously applied to small diameter cutterheads.
SUMMARY
The present invention relates to an improved rolling type disc cutter and to a method for mounting the cutter in a cutterhead assembly. Our novel disc cutter and cutterhead designs provide:
improved disc cutter geometries;
high footprint pressure;
improved hard metal insert configurations;
improved disc cutter bearing designs;
more robust structural supports for the cutter;
simplified cutter mounting apparatus and methods;
small diameter cutterheads with disc cutters; and
improved cutter rebuilding methods.
In addition, the disc cutter of the present invention provides higher penetration into any given rock at lower thrust than conventional disc cutters. This performance factor at lower thrust is very significant in many types of excavating machinery design. The lower thrust requirements possible by use of our designs allow lighter excavating machine structural components, as well as lower operating power requirements for a given excavation task. Moreover, more mobile excavating equipment.
In practice, it is in smaller diameter cutterheads (in drilling, the entire cutterhead is sometimes referred to as a bit) that some of the most dramatic increases in performance may be achieved by the present invention. For example, in small diameter cutterheads or bits, by using our disc cutter and cutterhead design, the specific energy required for drilling can be reduced by about an order of magnitude, for example, from about 80 HP-hr/ton to about 8
HP-hr/ton. Also, our disc cutter and cutterhead, by providing larger average chips, can achieve an excavation rate (lineal feet per hour) which is improved by about a factor of ten (10) over drill bits known heretofore.
We have developed a novel rolling disc cutter for use in a mechanical excavation apparatus to exert pressure against substantially solid matter such as rock, compacted earth, or mixtures thereof by acting on the rock or earth face. The cutter is of the type which upon rolling forms a kerf by penetration into the face so that, by using two or more cutters, solid matter between a proximate pair of said kerfs is fractured to produce chips which separate from the face. The disc cutter components include a relatively stiff shaft defining an axis for rotation thereabout, a proximal end for attachment to the excavation apparatus, and a distal end at or near which a cutter ring is rotatably attached. A cutter ring assembly, is provided, wherein the cutter ring assembly further includes an annular cutter ring having an interior annulus defining portion and an outer ring portion.
The outer ring portion includes a cutting edge having to substantially fit into the annulus defined by the cutter ring, and (2)in a close fitting relationship with the s.naft, so that the cutter ring may rotate with respect to, and be supported by said shaft, with minimal deflection of the shaft. The bearing assembly includes a bearing, and a seal.
The seal is adapted to fit sealingly between the cutter ring and an external hard and polished washer surface, provided integrally with the shaft or optionally provided by a hard washer ring. The seal provides a lubricant retaining and contamination excluding barrier between the cutter ring and the shaft or shaft support structure.
A retainer assembly, which includes a retainer plate and fasteners to affix the retainer plate to the include a (i) substantially continuous engaging contact portion of radius R1, wherein the contact portion on the outer side of said inserts are adapted to act on said face, (ii) a lower groove insert portion, which has a bottom surface shaped and sized in complementary matching relationship relative to said bottom surface of said groove, and first and second opposing exterior side surfaces which are shaped and sized in a complementary matching relationship relative to the interior walls, (iii) a rotationwise front and rear portion. The lower groove insert portion of the inserts fit within the groove in a close fitting relationship which defines a slight gap between the inserts and the interior walls.
A somewhat elastic preselected filler material such as a braze alloy is placed between and joins the inserts in a spaced apart relationship to the groove bottom and to the interior sidewalls. The preselected filler material is chosen so that it has a modulus of elasticity so that in response to forces experienced during drilling against a face, the inserts can slightly move elastically relative to the cutter ring so as to tend to relieve stress and strain acting on the insert segments.
OBJECTS, ADVANTAGES, AND NOVEL FEATURES
The present invention has as its objective the provision of an improved bearing design for disc cutters which reliably improves cutting rates at commonly encountered thrust pressures.
It is therefore an important feature of this invention that the disc cutter and cutter head design provide a bearing and seal arrangement in a small diameter rolling disc cutter which can reliably handle both axial and radial forces encountered during disc cutter operation.
It also an important object of this invention to provide a simplified cutter head design which reduces the cost of operating and maintaining rolling disc cutters, particularly by using simple and lightweight disc bearing and seals which are easily replaced.
It is therefore a feature of our disc cutter invention that the weight and complexity of disc cutter is significantly reduced, enabling the provision of reliable, yet very small diameter disc cutters.
Another important object of our invention is te meet or exceed the rock cutting performance of prior art large, heavy, 17 inch (43.18 cm) or larger rolling disc cutters with a small diameter, light-weight disc cutter.
It is accordingly an important feature of our invention that our rolling disc cutter may be completely assembled, disassembled, and serviced with common hand tools by a single workman, without resort to heavy lifting equipment.
It is a still further object of this invention to disc cutter so that disc cutter technology may be extended to small diameter cutterheads and to drill bit bodies.
A further objective of this invention is to provide a robust cantilever mounting method which permits close kerf (concentric cutter track) spacing, in order to facilitate close spacing of rolling cutters on small cutterheads.
A related objective is to achieve the ability to space rolling disc cutters quite close together, without resort to multiple row arrangements for cutter sets.
It is a further objective of this invention to provide a recessed cutter type mount which may be directly welded into the cutterhead structure, thus avoiding the necessity to use saddle or two sided type disc cutter mounting.
It a a related objective of this invention to provide use of recessed disc cutter mounting methods for manufacture of a shielded type cutterhead that is suitable for use in broken rock or in soft ground with boulders.
A still further objective of this invention is to provide a cutterhead which quickly scoops up the rock cuttings, bringing them inside the head as they are created, thus eliminating inefficient regrinding of the cuttings.
Yet a further object of this invention is to provide a disc cutter which is easier to install and maintain than previously used disc cutters.
A still further object is to provide a disc cutter design which reduces the lateral, or axial thrust, so that the disc cutter does not require expensive, heavy, and excessive space consuming bearings and seals, but can
Yet another object of this invention is to provide an improved bearing design which may be easily pressure compensated for reliable lubrication of moving parts when in submerged operation.
A still further object of this invention is to provide a disc cutter head which makes it possible to reduce the size of a drill bit when utilizing our small diarneter disc cutter designs and technology.
Another object of this invention is to provide a carbide tipped disc cutter which wears at an optimum rate and in an optimum pattern to maintain cutting efficiency throughout the life of the cutter.
Yet another object of this invention is to provide a hard insert such as tungsten carbide in a geometry which preserves the disc cutting efficiency by the use of improved continuous segments.
Finally, in is inevitable that still further objects of the invention will be apparent after full review of this specification and accompanying drawing and claims.
Accordingly, the invention provides a number of improvements, including a superior small diameter disc cutter design, an improved drilling method incorporating the use of the superior small disc cutter design, and an improved carbide bit for the disc cutter which maintains high cutting efficiency throughout the life of the cutter.
DESCRIPTION
The present invention will now be described by way of example, and not limitation, it being understood that a small diameter rolling type disc cutter with a long wearing blade, and cutterheads advantageously employing the same, may be provided in a variety of desirable configurations in accord with the exemplary teachings provided herein, including the use of various bearing and seal arrangements that reliably enable small diameter cutters to be utilized at relatively high radial loading, while withstanding the axial loadings encountered in the specific rock cutting service.
Basic Disc Cutter Details
Attention is now directed to FIGS. 7, where our novel disc cutter is shown by way of an exploded cross-sectional view, to FIG. 8, where the same embodiment is shown in a perspective view, and to FIG. 9, where the same embodiment is shown in an assembled cross-sectional view. Our novel cutter will be easily understood by evaluation of these three figures.
The cutter 120 is comprised of five (5) major parts:
First, a large diameter shaft 122 is provided.
Second, a washer surface 123, preferably hardened, is required. (Washer surface 123 is here shown as provided by optional ring type washer 124 rather than provided as an integral washer surface 125 as part of the shaft 122 structure, as seen in FIG. 7A.) assembled, nested within the cutter ring assembly 126 are the cutter ring 128, bearing 130 (including inner 132 and outer 134 race) and seal 136 (here all shown individually in exploded view). The cutter ring 128 is the ring which runs against a rock to be cut and imparts the cutting action described above.
Fourth, a retainer 138 retains the ring assembLy 126 onto the shaft 122. Retainer 138 is secured in place by fasteners such as machine screws 140, which in turn pass through fastener apertures in retainer 138 and are received by threaded receptacles 142a, 142b, and 142c (see FIG. 8) in the end 144 of shaft 122.
Fifth, a hubcap 146 is affixed to the outer side 148 of cutter ring 128 by securing means such as threads 150 (on hubcap 146) and 152 (in cutter ring outer side 148)
Although threads 150 and 152 are shown, those skilled in the art will appreciate that other substantially equivalent securing means such as a snap ring arrangement may also be utilized. The hubcap 146 rotates with the cutter ring 128 and thus eliminates the need for an outer seal. The clearance between the interior wall 154 of hubcap 146 and the outer end 156 of fasteners 140 is minimal and prevents the fasteners 140 from backing out should they happen to loosen. The hubcap 146 also serves as a cover for an interior oil or grease reservoir 158 (see Fig. 9 ).
Thus, the overall cutter assembly 120, contains but five (5) major parts. This is a significant reduction in parts when compared to many conventional prior disc cutters heretofore known which contain as many as twenty (20) or reduced weight when compared to prior art disc cutters.
The hard washer 124 described above is utilized as a replaceable wear surface on which the seal 136 rubs.
However, it is to be understood that washer 124 is an optional part depending upon the selected use and desired economic life cycle of the disc cutter or body 120.
However, in the embodiment as illustrated in FIG. 7, when a ring assembly 126 is replaced, the bearing 130 and seal 136 are replaced as well. All wear components, except the above described hard washer 124, are thus contained in the single ring assembly 126. Yet, even the hard washer is easily accessed when the ring assembly 126 is changed, thus easy maintenance of the disc cutter 120 is achieved.
Disassembly of cutter 120 can be accomplished with use of simple, common hand tools. Reassembly of cutter 120 is accomplished with equal ease. The worn cutter ring assembly 126 which preferably weighs less than forty (40) pounds (18.14kg.); more preferably the cutter ring is provided in a weight less than twenty (20) pounds (9.07kg.); most preferably the cutter ring is provided in the range of three (3) pounds (1.36kg.) to eight (8) pounds (3.63kg.) (for a five (5) inch (12.7 cm) diameter disc cutter)
Therefore, the cutter assembly 126 weighs in the range of approximately one tenth (l/lOth) or less of the weight of conventional prior art disc cutters. Cutter ring assembly 126 is thus quite portable, even in quantity, and is easily handled in the field by a single workman without need of power lifting or carriage tools.
Also, the cutter ring assembly 126 is sufficiently inexpensive that a worn ring
To install a new ring assembly 126, the ring assembly 126 is slid onto the shaft 122, the retainer 138 is secured, and the hubcap 146 is installed.
Further details of the cutter 120 may also be seen in this FIG. 7. At the inward 160 side of shaft 122, a retaining wall 162 is provided. When a wear ring 124 is utilized, the outer edge 164 of the wall 162 is provided with a shoulder portion 166 sized in matching relationship with the inner wall 168 diameter of wear ring 124. Also, retaining pins 170 are provided to insert through ape:rtures 172 provided in wear ring 124, to secure wear ring 124 against rotation.
Seal 136 is sized to fit within a seal receiving portion 174 of cutter ring 128. An outer shoulder :76 of cutter ring 128 extends inwardly in the axial direction to the above (toward the outside) seal receiving portion 174.
The outer shoulder 176 includes a lower seal portion 178 and an inward surface 180.
Below the seal receiving portion 174 of cutte: ring 128 is a bearing retainer portion 182 which extends radially inward at least a small distance so as to prevent the advance of bearing 130 all the way through cutter ring 128 upon assembly. An interior sidewall 184 of ring 128 is sized in matching relationship to the outside diameter of the outer race 134 of bearing 130, so that the bearing 130 fits snugly against interior sidewall 184.
Retainer 138 may include an inwardly extending outer edge portion 186 which is sized and shaped to match the appropriate portions of the selected bearing 130 so as to bearing 130 in an appropriate operating position. Also, one or more lubrication apertures 189 may be provided to allow lubricant to migrate to and from lubricant reservoir 158 (see FIG. 9).
Hubcap 146 may include a threaded plug 188 for use in providing lubrication as selected depending upon the type of service of the disc cutter 120. As more clearly visible in
FIG. 8, hubcap 146 may be provided with a purchase means such as slot 190 for enabling application of turning force as necessary to turn the hubcap through threads 150 and 152 so as to tighten the hubcap. Also, hubcap 146 may also include a shoulder 191 or other diameter adjusting segment to allow internal clearance with retainer 138.
For underwater applications, a grease type lubrication system is normally provided with a pressure compensation membrane 192 and interconnecting lubricating passageways 194 defined by lubricating passageway walls 196.
Also seen in any of FIGS. 7, 8, or 9, a pedestal 198 is provided for integral attachment of the cantilevered shaft 122.
It is important to note that shaft 122 is of large diameter SD in proportion to the outside diameter OD of the cutter 120. For example, with a five (5) inch (12.7 cm) diameter OD disc cutter, the shaft 122 diameter SD would preferably be at least forty percent (40g) of the cutter 120 diameter OD, or at least two (2) inches (5.08 cm) diameter.
A large ratio of shaft 122 diameter SD to cutter diameter OD ratio is important to provide a sufficiently stiff shaft to minimize possible deflection of shaft 122. Nonetheless, we decrease the overall ratio to as low as about 30%, more or less, provided adequate shaft stiffness is provided for the particular service.
Our novel cutter 120 design can also be described in terms of the minimal radial space required for bearing purposes. Again, for an exemplary five (5) inch (12.7 cm) diameter OD cutter, when using a needle type bearing as illustrated in FIGS. 7, 8, and 9, the total bearing space (B2 + B2) would occupy about twenty percent (20%) of the total diameter OD (or also about twenty (20%) of the total radial space). The ratio of shaft diameter SD to cutter ring diameter OD is preferably over 0.4 (i.e, the shaft diameter is at least 40W of the cutter ring diameter) . More preferably, the ratio of the shaft diameter to cutter ring diameter is in the range of 0.4 to 0.5 (i.e., the shaft diameter SD is forty to fifty percent (40-50%) of the diameter OD of the cutter ring 128.
Using the desired shaft size or better in conjunction with the other design features illustrated provides extreme rigidity to the shaft 122, thus substantially minimizing shaft deflection when the cutter 120 is under load and thrusting against a rock face. Shaft deflection has historically been a major cause of early bearing failure in disc cutters, particularly when roller bearings were used as in the prior art device shown in FIG.
6 above. However, due to the unique operational characteristics of our novel disc cutters, as further described herein, we have found that in certain circumstances, it is desirable to decrease the overall ratio to as low as about 30%, more or less, provided adequate
With respect to the desirable size of cutters 120 in the design just illustrated, we can provide cutter rings 120 in various sizes. However, cutter rings of less than about twenty (20) inches (50.80 cm) diameter, and preferably in the range of about fourteen (14) inches (35.56 cm) diameter and smaller, and more preferably in the range of about nine (9) inches (47.29 cm) diameter or smaller, and most preferably in the five (5) inch (12.70 cm) diameter range or smaller, are desirable.
These sizes are considered practical for currently known applications, although our disc cutter design could be provided in any convenient size.
Laboratorv Testinq
The first tests of a five (5) inch (12.70 cm) diameter cutter fabricated in accord with the present invention were conducted on the Linear Cutter Machine (LCM) at the Colorado School of Mines. A sketch of the LCM is provided in FIG. 10. This test machine 202 simulates the cutter action of an excavating machine by passing a rock sample 204 beneath the test cutter 200. Depth of penetration Y and spacing S can be set, while forces in three axis are measured (rolling force 206, normal force 208, and side force 210) as indicated in FIG. 11.
The LCM 202 has a spacing cylinder 212 for lateral movement of the sample, as well as cylinders (not shown) for moving the rock sample 204 horizontally kerf wise under the cutter. The depth of cut (penetration Y) is controlled by placing shims 214 between the cutter mount 216 and the LCM frame 218. A load cell 220 measures the forces on the pedestal, not shown) below the load cell 220. The rock sample 204 (or 204') is held in a rock box 222, which is in turn supported on a sled 224 suitable for transport of the rock sample 204 back and forth, and at a desired spac.ing S (via way of spacing cylinder 212) below the cutter 200.
The nomenclature used for recording test data and general appearance of the rock sample 204 are set forth in
FIG. 12. In general, multiple cuts are made across rock sample 204 at spacing S, with penetration Y. Each complete pass (here shown as pass 1 through pass 5) results in removal from rock 204 a thickness Y.
Initial results are shown in TABLE I and TABLE II.
The first rock sample 204 used was an extremely hard gneiss (about 43,000 psi compressive strength) rock. The second rock 204' was a 23,000 psi compressive strength welded tuff.
TABLE I
Five (5) inch (12.70 cm) Diameter Cutter Performance
43,000 psi Rock
Pene- Spacing Avg. Thrust Avg. Side Specific tration Force Force Energy (inches (inches) (lbs) (lbs) HP-hr/yd3 0.075 0.75 8,515 332 31.9
1.00 9,613 599 29.1 0.100 0.75 9,968 533 30.5
1.00 10,347 721 24.4 0.125 0.75 10,878 828 30.2
1.00 11,103 834 23.7
TABLE II
Five (5) inch (12.70 cm) Diameter Cutter Performance
23,000 psi Rock
Pene- Spacing Avg. Thrust Avg.
Side Specific: tration Force Force Energy (inches (inches) (libs) (lbs) HP-hr/ycl3 0.10 1.5 8,062 316 11.08
2.5 8,217 367 7.79
3.0 9,102 384 7.43 0.15 1.5 8,845 566 10.2
2.5 11,379 762 7.04
3.0 11,956 302 6.61
Conclusions from Testinq and Relevance to Key Desiqn Obiectives
Those experienced in disc cutter application and testing will appreciate that the thrust and side forces of our novel disc cutter, as set forth in the test data in
TABLE 1 and TABLE 2, are extremely low in comparison with those forces which would be experienced with a conventional disc cutter, such as a 17 inch (43.18 cm) disc cutter of the type shown in FIG. 6 or in the in the Fikse patent, for example.
TABLE III below shows comparison results in the same rock (23,000 psi welded tuff) between our disc cutter design and a disc cutter designed by the Robbins Company (similar to that shown in FIG. 6 above), when both cutters operate at a spacing of three (3.00) inches (7.62 cm). As is evident from TABLE III, our novel cutter achieves the same penetration with substantially reduced thrust. Also, our cutter accomplishes the same penetration with substantially reduced side loading, here a little less than three (3) percent of thrust, as compared to about ten (10) percent on the prior art Robbins Company cutter.
The significance of this thrust reduction can be readily understood by considering a nominal six (6.0) foot (182.88 cm) diameter cutterhead. If a three (3) inch (7.62 cm) kerf spacing across a rock face were desired, a typical six (6.0) foot (182.88 cm) cutterhead would have fourteen (14) cutters and might rotate at about twenty (20) revolutions per minute ("rpm"). If conventional seventeen (17) inch (43.18 cm) cutters were used, as based on the data
14 x 42,200 = 590,800 pounds force
If our novel disc cutter as described herein were used, the total thrust would be:
14 x 11,956 = 167,384 pounds force
In both cases, the boring machine penetration rate th:rough the rock would be equal, at 0.15 inches (0.38 cm) per revolution, or fifteen (15) feet (457.2 cm) per hour.
Yet, the thrust required for prior art excavating equipment using prior art type seventeen (17) inch (43.18 cm) disc cutters is 590,800 pounds force, while the thrust requirements or a cutter head using our novel disc cutter design is only 167,400 pounds force. Therefore, it can be appreciated that substantial reductions in excavation equipment struct:ure, weight, thrust cylinder size, and operating power requirements are made possible by use of our novel disc cutter design.
TABLE III
COMPARISON WITH PRIOR ART CUTTERS
Cutter Type Penetration Thrust Side Force
(inches) (lbs. force) (lbs)
Our new 5" (12.70 cm) cutter 0.15 11,956 302
Robbins Co.
17" (43,18 cm) cutter with 0.5" (1.27 cm) wide blade 0.15 42,200 4,200
Note: Spacing ("S") = 3.0 inches (7.62 cm)
Referring now to FIG. 7B, preferably our novel disc cutter ring 240 is provided with a blade width W of less than about one-half (0.5) inches (1.27 cm) , and more preferably, our novel cutter ring 240 is provided with a blade width of less than about 0.4 inches (1.02 cm), and most preferably, a relatively thin blade (0.32" to 0.-S" or 0.81 cm to 0.89 cm in width) is provided. The most preferred blade width penetrates into a rock with less thrust force requirement than the one-half inch (1.27 cm) and large width blades (0.5" to 0.8" or 1.27 cm to 2.03 cm blade widths most commonly used) found in conventional prior art disc cutters.
Also, our relatively small cutter blade ring 240 outside diameter OD - preferably in the five inch (12.70 cm) range - as well as the preferably substantially smooth transverse cross-sectional shape, more preferably sinusoidal cross-sectional shape, and most preferably semi-circular transverse cross-sectional shape of the cutter blade tip (here shown with a radius R7) reduces side loading. Whereas conventional cutters normally show a side load of about one tenth (0.1) of the thrust load, our new cutter ring 240, and similar cutter ring 128 discussed above, provides a side load somewhat less than one tenth of thrust load , and generally provides a side loading of about 0.06 times the thrust loading, or less.
The reduced side loading has allowed utilization of novel bearing construction in our rolling disc cutters. The bearing means utilized can be any one of a variety of
We have found that with the relatively low side loads encountered, a needle type bearing provides sufficient bearing capability at relatively low cost. The needle type bearing accepts a high thrust load at low speeds (generally under 200 RPM) but is not tolerant of high side loading or axial loads. Therefore, our cutter design which minimizes side load is significant in reducing bearing costs and important in attaining adequate overall reliability of the bearing.
One bearing make and model which has proven to provide satisfactory service during our testing has been a
Torrington model 32 NBC 2044 Y2B needle bearing, which is used with a Veriseal teflon type seal manufactured by
Busak+Shamban model S 67500-0177-42.
Use of the needle type bearing achieves one key design objective of our cutter because it requires a very small amount of radial bearing space, noted, for example, as
B2 above in FIG. 7. The needle type bearing is particularly an improvement over the double row, tapered roller bearings design used in prior art cutters such as is illustrated in
FIG. 6 or in the Fikse patent. The radial space thus saved by our bearing design allows the use of a relatively large diameter shaft, thus enabling achievement of another key design objective. The large shaft minimizes shaft deflection when under load, to a degree which easily permits the use of a cantilever mounted cutter assembly, rather than saddle mounted cutter assembly. The cantilever shaft (axle) arrangement also helps achieve another key design objective, namely simplified assembly and disassembly of the cutter.
Finally, the cantilever axle mounting arrangement allows the provides close kerf spacing, as frequently desired in rock drilling type applications.
ImProved Cutter Ring Desiqn
The cutter ring 128 is the component which is pushed with great force against the rock face, and which causes the rock chipping action. The cutter ring 128 (or similar ring 240 as in FIG. 7B) is thus subject to wear, which is greatest when the cutter ring 128 attacks a rock containing quartz and other hard crystalline minerals. Nevertheless, a simple alloy steel ring 128, as illustrated in FIGS. 7, 8, and 9, when hardened to 57 - 60 Rockwell "C", is satisfactory in limestone, for example. However, such a hardened cutter ring 128 shows signs of rapid wear in a welded tuff material containing 25 - 30% quartz. Therefore, when excavating such materials, a much harder, wear resistant cutter ring material is highly desirable.
FIG. 13 shows a cross-sectional view of another embodiment of our novel disc cutter in which a cutter ring 250 is provided which has a hard metal insert 252 as the cutting edge, or blade 254. This cutter blade 250 design not only wears longer than the above described alloy blade 128, but it is also "self sharpening."
As the hard metal insert 252 wears, the metal walls 256 and 258 which support the insert 252 also wears, to shapes shown as 256' and 258' in FIG. 14. However, the blade 254 width W remains constant, as is illustrated in the worn blade 254' illustrated in FIG. 14.
In contrast to our novel hard metal cutter blade 254 as common prior art button type insert cutters, present an increasingly blunter cutter surface to the rock as wear progresses. FIG. 15 illustrates such a prior art all metal disc cutter 260 with a tip 262 width Wop¯1 when new. This is similar to the prior disc cutter shown in FIG. 6 above.
After substantial wear, the result is a broadened and flattened cutter blade 262' of width Wop¯2, as shown in FIG.
16. Thus, FIG. 16 illustrates a standard wear pattern which is normally evident in prior art all metal type disc cutter blades, when ready for blade replacement. The worn cutter blade width Wop 2, being wider than the new cutter blade width Wop¯1, will, with equal pressure, not penetrate the rock as well. This increasing cutter blade width accounts for the significant and well known drop off of performance as prior art cutters wear out.
Another technique which has heretofore been tried by others for enhancing cutter life is illustrated in FIG. 17 and 17A. Button type inserts 270, with conical or chisel shaped outer ends 272, were inserted into cutter rings 274.
Unfortunately, the button end 272 and the edge 276 of ring 274 became rather flat, as best seen by the shape of edge 276' in FIG. 17A. Therefore, although the wear life may have been enhanced to some limited degree in that design, the ultimate result was still a precipitous drop off in rock cutting performance as the cutter wore out. Further, a common failure occurred by shearing off the carbide button as the metal supporting structure wore away.
In contrast to prior art designs, FIG. 19 shows an axial cross-sectional view of our novel disc cutter design to cut at the bottom position 281) which was successfully tested at the Colorado School of Mines Laboratory. This embodiment is essentially identical to the embodiment first illustrated in FIGS. 7, 8, and 9 above, except that prior cutter ring 128 is here replaced by cutter ring 280. The cutter ring 280 includes a disc shaped body 282 having an outer edge 284. The body 282 includes opposing outer side wall portions 286 and 288. The opposing outer side wall portions 286 and 288 each further include an interior wall, 290 and 292, respectively, and an exterior wall, 294 and 296 respectively.
The body 282 also includes a bottom edge surface 298 which interconnects with the interior walls 294 and 296 of the opposing outer side wall portions 28 D and 288. The opposing outer side wall portions 286 and 288 extend substantially radially outwardly relative to the bottom edge surface 298 to thereby define a peripheral groove 300 penetrating the outer edge 284 of the disc shaped body 282. The interior walls 294 and 296 are spaced above the bottom edge surface 298, preferably so that the walls 294 and 296 extend adjacent in close fitting fashion a 302 must be carefully configured in order to achieve long service life, as the precise size and shape of the inserts have considerable influence upon their longevity.
To that end we have done considerable work and investigation, the results of which are set forth herein, in order to determine an exemplary insert 302 shape which results in an acceptable service life. Set forth in the transverse cross-sectional view of FIG. 18 is one possible configuration for providing hard metal inserts 302.
In FIG. 18, it can be seen that twelve (12) inserts 302, each substantially in the shape of a segment of an annulus having an outer diameter R1 and an inner diameter R2, can be provided for mounting on a cutter ring 280 with shaft radius of size Rg and insert slot radius R2,. While it may be desirable to have the inserts 302 built in circumferentially larger angular segments, or even as a single annular piece, in view of current tungsten carbide insert manufacturing techniques, extremely large angular segments would be rather difficult to produce.
However, a hard metal insert design with at least as few as four segments 302', as illustrated in similar transverse cross-sectional view FIG. 18C, is believed feasible utilizing current manufacturing technology and the design techniques taught herein.
The precise configuration of each segment 302 was also the subject of research, as we found that it was necessary to carefully construct the segments in order to avoid their premature failure. We have discovered that is is significant in the design of the outer surface 310 of each hard metal insert segment that careful attention be
FIG. 18A, R1 is the desired radius of the cutter disc: 280 (for example, 5 inches (12.70 cm) outside diameter OD in one tested embodiment) . The bottom 312 of insert 302 has a radius R2, which is sized and shaped to match groove 300, formed by bottom 298 wall of radius R2r and side walls 290 and 292 of radius R8. With cutter rotating in the direction of reference arrow 314, a trailing edge 316 of the segment 302 is provided with a curvature R3 which is slightly reduced from radius R1.
At the end 318 of insert 302, another well rounded radius R5 is required. We have found that it is desirable that R5 be no less than about 0.065 inch (0.17 cm) when R1 is five (5) inches (12.70 cm)
Normally, segments 302 are manufactured symmetrically, and therefore leading edge 320 is provided with radii R4 and
R6, which preferably correspond to radii R3 and R5, respectively. Without use of curved portions including each of the mentioned radii, any insert segments superficially similar to exemplary segments 302 have been found subject to premature cracking or catastrophic failure.
In addition to the just described radii, it is important to provide a slight gap 322 between hard metal segments 302. Because the co-efficient of thermal expansion of steel alloy cutter ring 280 and the hard metal inserts 302 are different, temperature cycling will crack the segments 302 unless slight relative movement is allowed between the segment 302 and the cutter ring 302. The selected fabrication method must allow for this minute movement to occur.
Also, the finite thickness T (R2 - R2,) and ductile solder 330 used to secure the segments 302 is significant.
This finite thickness T and ductile composition both cushions the hard metal inserts 302 and allows the small relative movement between the hard metal inserts 302 and the base cutter ring 280 material.
Variations in the size of the hard metal insert 302, but still showing the overall desired smooth, rounded, preferably sinusoidal, and most preferably semi-circular (with radius R7,) transverse cross-sectional shape of insert 302, are shown in FIGS. 18B and 19A. A cutter 280 which is ready for rock cutting operations is illustrated with an external view in FIG. 20 (here considered as a top view in comparison to the side view provided in FIG. 19). Hard metal insert segments 302 in cutter ring 280 are illustrated in their working position, ready for rock cutting operations.
During tests, a disc cutter 400 with cutter ring 280 having hard metal insert segments 302 installed as shown in
FIGS. 18 and 20 exhibited virtually identical performance to a new, solid steel cutter ring (ring 128 above) . The continuous blade formed by hard metal inserts 302 performs as the principal contact surface between the disc cutter 400 and the rock being cut, without significant gaps in contact between the rock and the hard metal inserts 302 during rolling action of the disc cutter ring 280.
In contrast to our disc cutter, conventional cylindrical "button" inserts (see FIG. 17 and above discussion) perform in an impact mode, and penetrate rock in a cratering fashion. That impact mode of rock excavation concluded by reference to FIG. 2 above, such prior art button type inserts consume greater amounts of energy to excavate a given volume of rock than our disc cutter, particularly when continuous segment hard metal inserts 302 are used, as illustrated in FIGS. 18 and 20.
Moreover, as our hard metal insert 302 design preserves the efficient cutting action of a true rolling disc cutter over the working life of the cutter, (i.e., as insert 302 wears, the cutting radius R7 shape is substantially preserved during wear thereof to maintain a substantially uniform cutter footprint) we prefer using such hard metal insert type blades for most rock excavation applications.
To confirm the durability of our insert segment type cutter blade design, we conducted tests on the LCM (described above) at Colorado School of Mines. The insert segment cutter 400 of FIG. 20 was tested using carbide inserts 302 on a hard rock sample (43,000 psi unconfined compressive strength) at increasing penetration depths until failure of the segments 302 occurred. Finally, at an average thrust load of nearly 30,000 lbs. (and peak load of over 50,000 lbs.) and at a penetration of 0.30 inches (o.76 cm), a hard metal insert 302 failed.
To illustrate the significant improvement in the state of the art which is provided by our novel disc cutter design, a computer simulation was used to estimate the force which would be required on a standard prior art seventeen (17) inch (43.18 cm) disc cutter to achieve 0.30 inch (0.76 cm) penetration in 43,000 psi rock. The computed force is over 100,000 lbs. thrust. However, on a prior art: disc available materials of construction. Therefore, it can be appreciated that our disc cutter can provide the superior wear characteristics of a hard metal cutter (usually tungsten carbide) at rock penetration depths superior to any rolling disc cutter heretofore available.
The ability of our novel disc cutter design to provide superior rock penetration at reduced thrust levels directly translates into the ability to cut rock at advance rates (i.e. lineal feet of rock cut per hour) superior to any disc cutter or cutterhead apparatus currently known to us.
In further confirmation of the excellent, and indeed striking improvement in the state of the art provided by our novel cutter design, the computer simulation further showed that at 30,000 lbs. thrust load, the standard prior art seventeen (17) inch (43.18 cm) cutter would penetrate only 0.03 inches (0.76 cm), or about one tenth (1/10) of the rock penetration of our new disc cutter 400 design. Thus, our new cutter 400 design has the potential of increasing penetration Y on a cutterhead or drill bit by a factor of 10, when operating at a comparable thrust loading.
This superior performance was demonstrated in the
Colorado School of Mines laboratory on a full scale (32 inch (81.28 cm) diameter) drill cutterhead 420, of the type illustrated in FIGS. 21 and 22. Cutterhead 420 is mounted on shaft 421 to provide rotary motion to the cutterhead 420.
As shown, cutterhead 420 contains twelve (12) of our five (5) inch (12.7 cm) diameter cutters 422. With 82.1 HP and 65,752 lbs. of thrust on the cutterhead 420, an advance rate of 33.6 ft/hr (1,024.13 cm/hr) was achieved in 23,000 psi
This is the best rock cutting performance in hard rock of which we are aware, and to the best of our knowledge, it is the best rock cutting performance ever witnessed in the
Colorado School of Mines laboratory on a cutterhead or drill bit.
Use of Small Diameter Cutters in Cutterheads
Although above in FIGS. 7, 9, and 19 above, our novel disc cutter 120 is shown mounted on pedestal 198, it is advantageous in some applications to avoid the use of a pedestal and instead directly affix the cutter 120 to a cutterhead. In FIGS. 21 and 22, the advantage of such an integral mounting technique can be seen in the construction of a protected, inset cutter arrangement which is particularly useful for drilling in broken ground or boulders. Cutterhead 420 is provided, and cutters 422 are mounted to body 424 via aft portions 425 of shaft 122. A cantilever mounted shaft 122 supports cutter 422 at or near the distal end of shaft 122.
As illustrated in FIGS. 21, 22, and 23, a further unique feature of a cutterhead 420 with integral shaft mounted cutters 422 is that cutter 422 to cutter 422 (kerfto-kerf) spacing S can be varied on a given cutterhead 420.
This is made possible (1) because the shaft 122 occupies a small frontal area on the body 424 of cutterhead 42cut, (in contrast to the total area required for use of a typical prior art saddle type cutter mount), and (2) because small diameter disc cutters are utilized, which enable the designer to incorporate a large number of shafts 122 ".n the additional cutters 422. Therefore, when it is desired to decrease kerf spacing S, additional disc cutters can be mounted on such extra shafts 122, and, in combination with the use of spacers 430 of width Z on existing cutter shafts 122, a new smaller kerf spacing S can be achieved.
In FIG. 23, it can be seen that a clearance H is left between the cap 146 of the cutter 422 and the cutterbody 424, so that cap 146 and retainer 138 may be easily removed and the cutter ring assembly 126 replaced as necessary.
With our novel cutter design, this replacement is easily accomplished with common hand tools.
Muck (cuttings) handling in our cutterhead designs is also simplified. That is because by placing muck scoops 426 on the front 427 of the cutterhead body 424, as well as side scoops 428 on the sides 429, the muck is picked up almost immediately, as it is formed. Thus, the regrind of the cuttings is substantially reduced, and therefore the efficiency of the cutter is greatly enhanced. With forward scoops 426, it is possible to gather up to 75% or more of the muck immediately, thus substantially improving cutter efficiency.
For micro-tunneling, box (blind) raising, raise drilling and tunnel boring, the problem of broken rock falling in on a cutterhead is a common and serious matter.
Shielded face cutterheads, where the rolling disc cutters are recessed, and in some cases can be removed from behind the cutterhead, have been known and have been developed by others for large diameter tunnel boring. Such prior art designs have been shown to be very effective in poor ground
Attention is now directed to FIGS. 24 and 25. Our disc cutter and cutterhead designs permit a dramatic improvement in shielded face cutterhead technology. Namely, we have been able to extend the use of shielded face cutterhead technology to much smaller diameter cutterheads.
Thus, shielded cutterheads with a novel and much simplified structural design are possible when using our disc cutter technology.
Two exemplary versions of our novel shielded cutterhead designs, which are configured so as to allow the loading, repair, or replacement of our disc cutters 422 from either the front (i.e, toward rock 448 face 449) or back (i.e., from behind the cutterhead), are shown in use in FIG.
24 (cutterhead 450) and FIG. 25 (cutterhead 452)
Configuration of cutterheads 450 and 452 were designed specifically for micro-tunneling in varying applications, ranging from solid rock 448 to soft ground with boulders.
As shown in FIGS. 24 and 25, our novel disc cutter see for example cutters 422a and 422b - can also be mounted by directly welding the cutter shaft 122 into a cutterhead 450 or 452. In that case, no saddle or pedestal is used, and the shielded, recessed cutter configuration, heretofore successful almost exclusively in tunnel boring applications can, by use of our novel cutterhead and small diameter rolling disc cutter design, be applied to much smaller micro-tunneling and drilling applications. Shielded cutterheads even in the two (2) ft. (60.96 cm) to four (4) foot (121.92 cm) diameter range are feasible, with about three (3) foot (91.44 cm) or slightly less diameter shielded cutterhead design greatly simplifies how broken ground (shielded type) cutterheads are fabricated, since easy rear (behind the shield) access to the disc cutters can be provided.
Another important design feature of our cutterhead 450 and 452 design is that it is hollow: it is built like a one-ended barrel. Gusset plates (braces) 462, located respectively inside cutterheads 452, also function as internal buckets. A disc cutter mounting saddle, as used by others heretofore, can be advantageously eliminated by use of our pedestal mount type disc cutter design, or by direct attachment to the cutterhead body, as noted above for our stiff shaft cantilever design. This combination of features dramatically simplifies fabrication as compared with typical prior art shielded cutterheads, which are typically fabricated with box section type or frontal plate type construction.
In FIG. 24, shielded type cutterhead 450 is shown set up for use in a drilling fluid application. The cutterhead 450 is rotated against face 449 by shaft means 464, which is in turn affixed to cutter head body by braces 460.
Cutterhead body 424 also includes a rear flange portion 466 which has an outer shield accepting flange 468. The shield accepting flange 468 rotates within the forward interior wall 470 of shield 472. A shield bulkhead 474 and shaft seal 476 prevent leakage of drilling fluid from flooded compartment 477 on the face 449 side of shield to the space rearward of the bulkhead 474. Drilling fluid indicated by reference arrow 478 is provided through bulkhead 474 to and through the cutterhead body 424, fluid picks up cuttings 482 and thence exits in the direction of reference arrow 484 past bulkhead 474 through outlet 486. The shield 4,2 and cutterhead 450 are advanced in a manner so that the forward interior wall 470 of shield 472 and the shield accepting flange 468 are maintained in shielding engagement with respect to the sides 488 of bore 490.
Another configuration for such an exemplary broken ground cutterhead is shown in FIG. 25. A nominal thirty two (32) inch (81.28 cm) diameter cutterhead 452 is illust--ated.
The hollow construction allows a muck removal system (not shown) to be inserted forward in the cutterhead 452, perhaps all the way to the inside 494 of cutterhead body 424, to a point as little as 8 inches (20.32 cm) from the rock face 449. The cutterhead 452 is compatible with a pneumatic muck system, or an auger, or a conveyor system. If an auger is used with a sealed bulkhead and water injector, the cutterhead 452 can be used as an EPB (Earth Pressure
Balance) type drilling apparatus. In such cases, the hollow cutterhead 452 becomes the essential muck chamber.
Cutterhead 452, as designed and illustrated, is thus suitable for use in drilling situations with high water inflow and hydraulic soil zones; it is also easily switched back and forth between the EPB drilling mode and an atmospheric or open drilling mode.
The cutterhead 452 set forth in FIG. 25 uses a downhole gear drive mechanism for providing rotary motion to cutterhead 452. The drive shaft 500 turns against a ring gear 502 which is affixed to cutterhead 452, and which, when bearing 504 separates the ring gear 502 and the shield support flange 506, to which shield 508 is attached. A roller type thrust bearing 510 is located between the shield support flange 506 and the bulkhead 512, to allow rotation of cutterhead 452 against the bearing 510, so that cutterhead 452 freely turns within the shield 508. Gear 502 and bearings 504, operate within an oil filled compartment 514, which is sealed by shaft seals 516 and by lip seal 520 between rotating bulkhead 518 and fixed bulkhead 522.
For most applications, a chevron type muck seal 524 is provided between the forward interior wall 470 of shield 508 and bulkhead 512, and/or the adjacent axially extending outer shield accepting flange 468 the rear flange portion 466 of cutterhead body 424.
Small Diameter Drill Bits
Attention is directed to FIG. 26, where one embodiment of our novel drill bit 530 design is illustrated.
As shown, the bit 530 is suitable for small bit sizes such as those in about the thirteen and 3/4 (13.75) inches (34.93 cm) in diameter range or so. The bit 530 incorporates six (6) of our novel five (5) inch (12.7 cm) diameter cutter discs 422. This bit 530, similar bits which are somewhat smaller, or those which are larger and range in size up to about twenty three (23) inches (58.42 cm) or so in diameter (about the largest standard size prior art tri-cone bit), can advantageously replace conventional tri-cone drilling bits.
due to use of our unique small diameter cutters 422. In the version of bit 530 illustrated in FIG. 26, six (6) of our novel disc cutters 422 are used to simultaneously cut into rock 448, at face 449, a bore 531 defined by borehole edge 532. Disc cutters 422 are outward (cutters 422i, 422j, 422k, and 422m) , to provide the cut; those familiar generally with use of prior art rolling cutters will recognize that the exact placement of cutters 422 may be varied without departing from the teachings of our novel bit design. Usually a drill string 533 (shown in phantom lines) is provided to provide rotary motion to the bit 530 by connection with drill head 534 of bit 530. The drill head 534 is connected to a downwardly extending structure 536 (normally steel).
The exact configuration of structure 536 is not critical, but may consist of a top plug structure 537, downwardly extending sidewalls 538, and the cutterhead assembly 539. Affixed below the cutterhead assembly 539 are disc cutters 422. Although we presently prefer to use a cutter pedestal 198 for each cutter 422 in order to maximize flexibility in number and location of cutters 422, other mounting configurations, such as described elsewhere herein, are feasible. Stabilizers 540 are affixed to the outward edges 541 such as at sidewalls 538 of structure 5.6 to position and secure the bit 530 with respect to borehole edge 532.
Because of the relatively low friction between the rolling disc cutters 422 and the rock 448 at face 449 and due to the relatively good heat dissipation by the rolling disc cutters 422, bit 530 can be used "dry", i.e., using dry mode, bottom cleaning of borehole 531 is accomplished by circulating a gaseous fluid such as compressed air. The air functions as both a cooling fluid and a muck or cuttings 542 transport media. Compressed air is supplied through a delivery tube 544 in the direction of reference arrow 546.
The fluid enters the face area muck chamber 548 through a "blast hole" orifice or nozzle 550. Fluid is expanded into the face area 548. Cuttings 552 are forced out the muck pick up tube 554, in the direction of reference arrow 555, by air pressure or by vacuum. When desired, by use of both air pressure and vacuum, the pressure P in the face chamber 548 can be controlled. Additionally, it can readily be appreciated that the bit 530 can be converted to "wet" operation simply by supply of a liquid drilling fluid, instead of air, downward through tube 544, and sending the cuttings upward through muck tube 554.
The advantage of bit 530 and of our novel small diameter cutterhead design generally for use in conventional drill bit applications can more readily be appreciated by reference to recent test data. A typical tri-cone drilling bit was tested in cutting (a) aged hard concrete and (b) basalt, where, as is typically done, fine cuttings were produced. In aged hard concrete (about 6,000 psi strength) the tri-cone bit cut at a specific energy of 80 horsepowerhour per ton. In basalt (about 35,000 psi strength) the tri-cone bit operated at 120 horsepower-hour per ton.
Referring now to TABLE I, it can be seen that in tests conducted at the Colorado School of Mines, our novel disc cutter design, when operating on 43,000 psi rock at energy requirement between roughly twenty four (24) and twenty nine (29) horsepower-hours per cubic yard, (approximately 12 and 14.5 HP-hr/ton) depending upon the penetration Y achieved. In the same tests, when operating on 23,000 psi rock at one and one-half inch (1.5) (3.81 cm) spacing, our novel disc cutter achieved a specific energy requirement of ten (10) to eleven (11) HP-hour per cubic yard (approximately 5 to 5.5 HP-hr/ton).
Thus, by comparison of the specific energy requirements of prior art tri-cone drilling bits, and the specific energy of required for use of our novel disc cutters and cutterheads, one can readily appreciate that our novel disc cutter, when applied to a small drilling bit body such as bit 530, has the potential of improving the penetration rate by a factor of ten (10) or more at the same power input level.
Core Tvoe Drill Bit
Attention is now directed to FIG. 27, where a unique coring drill bit 600, again using our novel disc cutters 422, is shown in cross-section. FIG. 28 shows a face view of bit 600, (taken looking upward from the line of 28-28 of
FIG. 27.
In many respects, the core bit 600 is similar to bit 530 just described above, and with respect to such similar details, a detailed description need not be repeated for those skilled in the art to which this description is directed. In the core bit 600 as illustrated, six (6) of 422 are used (only three visible in this FIG. 27 crosssectional view - see FIG. 28 for further details) to simultaneously (a) drill a thirteen and three-quarters (13.75) inch (34.93 cm) diameter bore 602 defined by borehole edge 604 and (b) capture a four (4) inch (10.16 cm) diameter core 606. It can be readily appreciated that the dimensions provided are for purpose of example only, and are not in any way a limitation of the unique core drilling concept disclosed and claimed herein.
Disc cutters 422q and 422r are angled outward, and cutter 422s is angled inward, to provide the desired annular, core 606 creating cut.
The drill head 614 (not completely shown here but similar in structure and function to that used in bit 530 above) is connected to a downwardly extending normally steel structure 616 to support the bottom cutter head assembly 618. Affixed below the cutter head assembly 618 are disc cutters 422, preferably by way of a cutter pedestal 198 for each disc cutter 422. Stabilizers 620 are affixed to the outward edges 621 of structure 616 to position and secure the bit 600 in the borehole 604.
Again, because of the relatively low friction between the rolling disc cutters 422 and the rock 448 at face 449, and due to the relatively good heat dissipation by the rolling disc cutters 422, bit 600 can be used "dry", i.e., using only air as the cuttings removal fluid. Operation is basically as described for bit 530 above, whether used "dry" or "wet."
In the center of the bit 600 grippers 629 of core catcher 630 secures the core 606 as it is formed. When the core length, depending upon bit 600 dimensions) the stab 632 is sent down the hole 602, assisted by weight 631. Height 631 is connected to stab 632 by connection means such as shaft 633. The stab 632, by way of latch 634, fastens onto the core catcher 630.
Latch 634 may include core catcher locking means such as latch pivot arms 636 and springs 638 for urging pivot arms 636 upward so as to prevent stab 632 from becoming disengaged from the core catcher 630 when the stab 632 is pulled up the bore 602 and is pulled to the surface upon completion of one drilling "stroke," using a wire line (not shown).
As mentioned above, bottom hole cleaning is accomplished by a circulating fluid, such as compressed air.
Another unique feature of drill bit 600 is that both bore 602 and core 606 are located in dead end chambers.
Particularly when air is used as the drilling fluid, no significant air or muck flow passes by either the core surface or the inside surface of the bore. ..huts, contamination of either the core or bore is minimized, and an extremely clean core sample can be obtained by use of bit 600.
The performance of this core bit is expected to be far beyond ordinary diamond or carborundum type core bits.
As can be seen from the performance test of TABLE I, at 0.10 inch (0.25 cm) penetration and 1.5 inch (3.81 cm) spacing, for example, and assuming 60 rpm, penetration of thirty (30) feed per hour is expected in rocks of about 25,000 psi compressive strength.
Cutter Repairs
In addition to the above described performance increases anticipated of about a ten fold drilling rate improvement, drill bits using our novel disc cutters are simple to rebuild. This markedly contrasts to prior art tri-cone bits, well known in the art, which are rebuilt in the following steps:
a. Saw the bit body into three sections.
b. Destructively remove the three cutters and pedestals.
c. Machine, jig and dowel the three bit body sections.
d. Install new cutters and pedestals, one on each section.
e. Re-weld the three sections.
f. Re-cut the threads.
g. Hard face cutting zones as required.
The rebuild process of prior art tri-cone bits is time consuming (several days or more), and requires a well equipped machine shop. Also, and the refurbished bit sells for about 75% of the cost of a new bit of equivalent size.
* In contrast, when our novel disc cutter and drill bit design is used, the rebuild may be quickly accomplished in the field. By reference to FIG. 8 above, such a rebuild consists of the following:
a. Secure the bit (e.g. bit 600) [Mount the bit in a vise, or leave it on the drill rig].
b. Using a hammer, a wooden wedge and a crescent
(i) removing the cap 146 from the cutter ring 148
(ii) removing fasteners 140 from the retaining assembly 139;
(iii) removing the retainer 138
(iv) removing the cutter ring assembly 126 from the shaft 122;
c. Clean the unit and replace the hard washers 124 if required (such as if scored),
d. replacing the removed cutter ring assembly 126 with a new or reconditioned cutter ring assembly 126;
e. replacing the retainer 138 and said fasteners 140;
f. replacing the cap 146;
g. hard face zones, such as cutter 148 sidewalls, as required.
The operator of the drilling unit does the work with his own field labor, on site, with common hand tools. The work may possibly be done even while the bit is still on the drill rig. Such rebuild can be done in about one hour by one man. Moreover, if hard facing is not required, total elapsed time is a mere fifteen (15) minutes. For convenience of the operator, a repair kit can be provided which includes one or more of the various wear parts, such as a cutter ring assembly (or its components of a annular cutter ring, a bearing assembly including a bearing, and a seal), a retainer assembly, a hubcap, or hardened wear ring washer. The most likely replacement part would be the
Other Embodiments
Attention is directed to FIG. 29, wherein the use of journal type bearing 700 is shown.
This type of bearing 700 may be of the type with a base 702 and a wear face 704, or may be of unitary design. In some applications use of such a bearing 700 may further reduce the radial bearing space B2 required for our novel disc cutter 422, and such bearing 700 is entirely serviceable for certain types of cutter 422 applications. Also, a simple bushing type bearing is of similar appearance to bearing 700 and can be utilized as desired, depending u extend from a cutterhead body 706. Pedestals 705 are shaped to accept shaft 700. Caps 707 secure shaft 700 to pedestals 705 via use of fasteners 708. An end plate 710 secures retainer 712 to shaft 700 by way of fasteners 714. End plate 710 also locates and secures retainer 712, which in turn secures one of the two hard washers 124'.
Cutter ring 720 rotates about shaft 700 with cutting edge shape and performance as described above; also it is to be understood that the hard metal cutting edge as extensively described above can be adapted for use in an alternate cutter ring similar to ring 720, and need not be further described.
Also, as set forth in FIG. 31, journal type bearings 700 can be substituted for the needle type bearing 130 shown in FIG.
30.
During tests, a disc cutter 400 with cutter ring 280 having hard metal insert segments 302 installed as shown in
FIGS. 18 and 20 exhibited virtually identical performance to a new, solid steel cutter ring (ring 128 above) . The continuous blade formed by hard metal inserts 302 performs as the principal contact surface between the disc cutter 400 and the rock being cut, without significant gaps in contact between the rock and the hard metal inserts 302 during rolling action of the disc cutter ring 280.
Still further alternate embodiments may be desirable in order to provide a somewhat higher grade seal and bearing arrangement, as illustrated and described with respect to
FIGS. 32 through 36 below. Turning now to FIGS. 32 and 33, a rolling disc cutter 800 is provided with a relatively stiff shaft 802 having a proximal 804 and a distal end 806, 808 thereabout. More specifically, and as may be better seen in FIG. 33, a cutter ring assembly 810 is provided, including cutter ring 808 and bearing assembly 812. The cutter ring 808 has an interior annulus defining portion 814 and an outer ring portion 816 with a cutting edge 818 having an outside diameter OD (with radius R1).
The bearing assembly 812 is designed to substantially fit into the interior annulus portion 814 of the cutter ring 808, in a close fitting relationship with the annular wall 815 on one side and on the other with the external surface 816 of shaft 802, so that the cutter ring 808 may be rotated with respect to the shaft with anti-frictional assistance provided by the bearing assembly 812. A seal assembly 820 is provided to fit sealingly between the shaft 802 and cutter ring 808, so as to form a lubricant retaining seal for the interior chamber formed primarily by the interior annulus portion 814 of the cutter ring and primarily occupied by the bearing assembly 812. A retainer assembly 822, comprising a retainer 824 and one or more preferably threaded fasteners 826 are provided to retain the cutter ring assembly 810 on shaft 802.
This is preferably accomplished by having the inner edge 830 of retainer 824 positioned to resist any outward movement of the distal end 832 of at least the inner race 834 of bearing assembly 812.
Retainer 824 also is preferably provided with a lubricant passageway 835 which enables lubricants to flow from an interior reservoir LR outward through retainer 824. A cap 836 is provided; the cap 836 has an interior surface portion 838 which, in cooperation with the seal assembly and the provides a lubrication retaining chamber.
Lubrication is assured by use of a spring 840 actuated diaphram 842 to urge lubricants from reservoir LR into the chamber just described. For ease in understanding action of diaphram 842, in FIG. 33, for example, it is shown split in two. At the top 844 of reservoir LR, the reservoir
LR is shown full and with spring 840 and diaphram 842 compressed toward the proximal end 804 of shaft 802. At the the bottom 846 of reservoir LR, the reservoir LR is shown empty, with spring 840 extended fully toward the distal end 806 of shaft 802. Also evident in FIG. 33 the use of a pressure compensation system.
Filter 846 is a porous diaphram which allows external pressure to be hydraulically transmitted along passageways 848 and 850, so that any external hydraulic pressure can be allowed to act on diaphram 842, to thus pressurize lubricants in chamber LR, so that external contaminants such as water will not be urged past the seal assembly and into the aforementioned lubricant chamber. To assist in this task, diaphram 842 is preferably plastic and is provided with an o-ring type seal 852 at a peripheral groove, and chamber LR is provided with generally cylindrical shaped walls 854. For refill 1 of lubricants, a zerk type fitting 856 is provided, preferably through cap 836. In use, the zerk fitting 856 is preferably removed, and a socket type plug 858 is inserted in its place.
It is to be noted how easy it is to pressure compensate the cutter head in this novel arrangement. In particular, as seen when comparing FIGS. 32 and 33, pressure compensation can easily be provided either at the shaft 802,
When cap 836 is installed, exterior threads 860 are interfittingly engaged with interior threads 862 on in cutter ring 808. For additional security, a threaded locknut 864 is provided with interior threads 866 for interfitting engagement against exterior threads 860 on cap 836, in order to be secured against the distal side 868 of cutter ring 808, so as to lock cap 836 in place.
Seal assembly 820 includes a first 870 and a second 872 generally chevron shaped washer sealing surface ring, against the outer surfaces of which (874 and 876, respectively) a first 878 and second 880 o-ring type seals sealingly engage, respectively. As installed, this arrangement provides a full face type seal. Therefore, when in rotational service, the first chevron shaped washer sealing surface 870 is stationary, as is its accompanying o- ring seal 878. However the adjacent chevron shaped washer sealing surface 872, and its accompanying o-ring type seal, 880, rotate with the cutter ring 808. As a result, a faceto-face type seal is provided between seal surface 882 on chevron shaped washer sealing surface ring 870, and seal surface 884 on chevron shaped washer sealing surface ring 872.
Also note that the chevron shape of each of sealing surfaces 870 and 872, as well as their inward sloping surface 874 and outward sloping surface 876, respectively, enable the o-rings 878 and 880 to be advantageously compressed against an outward sloping flange 890 of shaft 802, and against inward sloping flange surface 892 of cutter ring 808, respectively. Ideally, an inward flange 894 on cutter ring 808 provides the required strength for inward when rotating. Also, it is preferrable that chevron shaped washer sealing surfaces 870 and 872 utilize hardened materials of construction, such as stellite or compa.rable materials. To protect inward flange 894 on cutter rinc 808, a second, generally L-shaped stage 895 of flange 890 is provided.
Preferably, bearing assembly 812 uses roller-ball type bearings, such as Torrington brand bearings number
NJA5910 or equivalent for the desired service size and load rating. Roller-ball type bearing include an inner race 834 and an outer race 896, with balls 898 therebetween, to provide for adequate strength and load capability. However, needle type bearings may be acceptable in certain service conditions.
Turning now to FIG. 35, yet another embodiment of my novel disc cutter is now illustrated. This embodiment is somewhat similar to the embodiment just illustrated in FIGS.
32 and 33 above, but now a seal is provided in a single or one-half face seal type configuration. In FIG. 35, a rolling disc cutter 900 is provided with a relatively stiff shaft 902 having a proximal 904 and a distal end 906, and a central axis denoted by C1 for rotation of cutter ring 908 thereabout. More specifically, a cutter ring assembly 910 is provided, including cutter ring 908 and bearing assembled 912. The cutter ring 908 has an interior annulus defining portion 914 and an outer ring portion 916 with a cutting edge 918 having an outside diameter OD (with radius R1).
The bearing assembly 912 is designed to substantially fit into the interior annulus portion 914 of the cutter ring 915 on one side and on the other with the external surface 916 of shaft 902, so that the cutter ring 908 may be rotated with respect to the shaft with anti-frictional assistance provided by the bearing assembly 912.
A seal assembly 920 is provided to fit sealingly between the shaft 902 and cutter ring 908, to form a lubricant retaining seal for the interior chamber formed primarily by the interior annulus portion 914 of the cutter ring and primarily occupied by the bearing assembly 912. A retainer assembly 922, comprising a retainer 924 and one or more preferably threaded fasteners 926 are provided to retain the cutter ring assembly 910 on shaft 902. This is preferably accomplished by having the inner edge 930 of retainer 924 positioned to resist any outward movement of the distal end 932 of at least the inner race 934 of bearing assembly 912. Retainer 924 also is preferably provided with a lubricant passageway 935 which enables lubricants to flow from an interior reservoir LR outward through retainer 924.
A cap 936 is provided; the cap 936 has an interior surface portion 938 which, in cooperation with the seal assembly and the interior annulus forming wall 915 of cutter ring 908, provides a lubrication retaining chamber.
Lubrication is assured by use of a spring 940 actuated diaphram 942 to urge lubricants from reservoir LR into the lubricant chamber just described. For ease in understanding action of diaphram 942, in FIG. 35 (and also in FIG. 36, but reversed) , it is shown split in two. At the bottom 944 of reservoir LR, the reservoir LR is shown full and with spring 940 and diaphram 942 compressed toward the reservoir LR, the reservoir LR is shown empty, with spring 940 extended fully toward the distal end 906 of shaft 902.
Also evident in FIGS. 35 and 36 is the use of a pressure compensation system. Filter 946 is a porous diaphram which allows external pressure to be hydraulically transmitted along passageways 948 and 950, so that any external hydraulic pressure can be allowed to act on diaphram 942, to thus pressurize lubricants in chamber LR, so that external contaminants such as water will not be urged past the seal assembly 920, or otherwise inward toward lubricant chamber such via threaded passageways. To assist in this task, diaphram 942 is preferably plastic and is provided with an o-ring type seal 952 at a peripheral groove 953, and camber
LR is provided with generally cylindrical shaped wall. 954.
For refill of lubricants, a zerk type fitting 956 can be provided, preferably through cap 936. When the disc cutter 900 is in use, the zerk fitting 956 is preferably removed, and a socket type plug 958 is inserted in its place (see
FIG. 36). It is to be noted how easy it is to pressure compensate the cutter head in this novel arrangement. In particular, as seen when comparing FIGS. 35 and 36, pressure compensation can easily be provided either at the shaf 902, or remotely on cutterhead 959.
When cap 936 is installed, a peripheral lip 960 is interfittingly engaged with interior groove 962 in cutter ring 908. For additional security, cap 936 may be tack welded 964 to cutter ring 908.
Seal assembly 920 includes a first 970 generally chevron shaped washer sealing surface ring, against the engages. As installed, this arrangement provides a single, or one-half type face seal. Therefore, when in rotational service, the chevron shaped washer sealing surface 970 rotates with cutter ring 908, as does its accompanying o- ring 978. A face-to-face type seal is provided between seal surface 982 at the distal end of chevron shaped washer sealing surface ring 970, and seal surface 984 on the proximal end of the inner bearing race 934. Also note that the chevron shape of the ring 970, as well as its outward sloping surface 974, and companion inward sloping flange 992 of cutter ring 908.
Ideally, an inward flange 994 on cutter ring 908 provides the required strength for inward reaching flange surface 992, against which o-ring 978 rides when rotating. Also, inward flange 994 also includes a substantially radially inward portion 995 which reaches to almost the outer surface 916 of shaft 902. Radially inward portion 995 has an interior surface 996 which cooperates with proximal end 997 of chevron shaped washer sealing surface 974 to discourage dirt entry to the o-ring 978 area.
Moreover, the distal end 982 of chevron shaped washer sealing surface 974 sealingly cooperates with the proximal end 984 of the interior bearing race 934 of bearing assembly 912 to provide the required lubricant seal. Again, it is preferrable that chevron shaped washer sealing surfaces 970 utilize hardened materials of construction, such as stellite or comparable materials.
Preferably, bearing assembly 912 uses roller-ball type bearings, such as Torrington brand bearings number
NJA5910 or equivalent for the desired service size and load and an outer race 999, with balls 1000 therebetween, to provide for adequate strength and load capability. However, needle type bearings may be acceptable in certain service conditions.
Turning now to FIG. 36, it can be be appreciated that the disc cutter 900 (as well as, for example, disc cutter 800) can be directly mounted on a cutterhead 420 as discussed hereinabove in conjunction with FIG. 23. Disc cutter 900 is mounted to body 424 of cutterhead via aft portions 425 of shaft 902. A cantilever mounted shaft 902 supports cutter 900 at or near the distal end of shaft 902.
Alternately, shaft 902 may be integrally formed with body 424 (such as by casting), so that areas labeled 902 and 425 in this FIG. 36 merge into an integrally formed common material.
As also illustrated in FIGS. 21, 22, and 23 above as well as this FIG. 36, a further unique feature of a cutterhead 420 with integral shaft mounted cutters 900 is that cutter 900 to cutter 900 (kerf-to-kerf) spacing S can be varied on a given cutterhead 420. This is made possible (1) because the shaft 902 occupies a small frontal area on the body 424 of cutterhead 420, (in contrast to the total area required for use of a typical prior art saddle type cutter mount), and (2) because small diameter disc cutters are utilized, which enable the designer to incorporate a large number of shafts 902 in the cutterhead body 424, for use in adding additional cutters 900. Therefore, when :t is desired to decrease kerf spacing S, additional disc cutters can be mounted on such extra shafts 902.
between the cap 936 of the cutter 900 and the cutterbody 424, so that cap 936 may be easily removed and the cutter ring assembly 910 replaced as necessary. With our novel cutter design, this replacement is easily accomplished.
Returning now to FIGS. 34 and 36A, the reader is reminded that the novel cutter rings 808 and 908 just discussed may also be provided in alternative designs with hardenend inserts 302. FIG. 34 shows cutter ring 808', similar to 808, but not utilizing a hardened insert design.
FIG. 36A is similar, showing alternative cutter ring 908' design for use with hardened inserts 302. FIG. 36A also shows the o-ring 978 and chevron shaped washer ring 970, as being inserted into the annular area of cutter 908', so as to engage surface 992 of flange 994. Particular attention should be paid to these embodiments, because it is an important feature of the present invention that cutters can be readily interchanged from use of a solid cutter ring (808 and 908) to use of hardened metal insert type cutter rings (808' and 908'). Another important feature is that in a particular cutterhead, the same size and type disc cutters can be used (a) in the middle of the cutterhead, (b) across the face of the cutterhead, and (c) around the gage (the periphery).
This is an important and unique feature, since in other cutterhead designs known to us, multiple disc cutter sizes are normally required for efficient cutting operation.
Still other bearing and seal arrangements may be utilized in order to take advantage of our unique small diameter rolling cutter design. Several additional bearing 40, all of which may be use advantageously for providing rolling cutters in bits, cutterheads, and other excavation equipment as described herein.
First, as noted in FIG. 37, a typical small diameter cutter 1100 preferably has a relatively large diameter shaft 1102. Cutter ring 1104 rotates about shaft 1102, with a bearing assembly 1106 and a seal assembly 1108 located between the fixed shaft 1102 and the rotating cutter ring 1104. The bearing assembly 1106 includes a pair of inwardly angled needle bearings 1110i and 1110o, which fit between inwardly centered angled inner races 1112i and 11120 and inwardly centered angled outer race 1114. A centering block 1116 provides spacing between inwardly centered angled inner races 1112i and 11120, as well as spacing between needle bearings 1110i and 1110o. The bearing assembly 1106 has an outer diameter BA and an inner diameter BI.
For one type of excavation service, I have found that inner diameter BI of approximately 1.181 inches (3.0 cm) is desirable, and an outer diameter BA of approximateluy 1.850 inches (4.70 cm), with a width BW of about 0.9055 inches (2.3 cm), or approximately so, is desirable. The thickness between outer diameter BA and inner diameter BI should be as thin as is feasible; the example given is using Torrington type 64X QB63226 needle bearings 1110i and 1110O. Bearing retainer 1118, secured by fasteners as earlier illustrated, secures bearing assembly 1106 in place. A hubcap 1119 can be press fit into place, as shown with ears 1119e interfacing with ring 1104r in cutter 1104, to encapsulate the inner lubricated space L.
This configuration provides an inwardly bearing assembly 1106 arrangement, and is able to minimize axial or thrust loading on the seal assembly 1108.
In the embodiment shown in FIG. 37, seal assembly 1108 has a single, inwardly facing generally chevron shaped ring 1120 with an outer sealing surface 1122, against which an o-ring type seal 1124 sealingly engages. The o-ring type seal 1124 also sealingly engages an inner sealing surface 1126 of inner flange 1128 of cutter ring 1104. Ideally, a radially inward tip 1130 of inner flange 1128 has an axially outward edge 1132 that engages inner edge 1134 of ring 1120, to accept axial loads.
In FIG. 38, yet another embodiment is illustrated, with an improved, unique bearing arrangement. Cutter 1200 has a central shaft 1202 with an interior passageway defined by inner wall 1204, sized to accomodate pressure compensation bellows 1206. The bellows 1206 serves to provide pressure compensation for lubricant 1207 in the reservoir behind bellows 1206 (to the right, as shown), in the manner described above. A peripherial flange 1208 of bellows 1206 is secured against land 1209 of inner wall 1204 and flange 1210 of bearing retainer 1212. Bearing retainer 1212 is annular in shape, with an inner threads 1214 adapted to threadedly engage threads 1216 of inner wall 1204 to allow retainer 1212 to be screwed inward to seal the bellows 1206 at flange 1208. The outward face 1218 of bearing retainer 1212 extends radially outwardly.
Bearing assembly 1222, including combination thrust washer/bearing retainer 1224 and needle radial bearing 1226, is unique in that the washer 1224 takes axial load in both directions. The washer in the outward direction, and against inward flange 1232 of cutter 1234 in the inward direction. In this edmbodiment, a "single" outwardly facing half-face seal asembly 1240 is provided, with chevon shape 1241 sealing ring with surface 1242, and o-ring 1244 acting between surface 1242 and inner sealing surface 1246 of cutter 1234. In this configuration,
I prefer to utilize a Torrington bearing model B-1916, needle bearing with combination retainer, and a Parker model 2-031 hubcap seal (HCS).
On one preferred embodiment, the hubcap seal diameter of about 1.8725 inches (4.76 cm) is provided, with a bearing retainer diameter BR of about 1.6 inches (4.06 cm), and a bearing assembly outer diameter BA of about 1.457 inches (3.70 cm), and a bearing assembly inner diameter BI of about 1.181 inches (3.0 cm) . The bearing retainer 1212 can have an outer flange thickness BRW of as little as 0.10 inches (0.25 cm), more or less. As shown, the hubcap 1250 is held on with a thin retaining wire assembly RW. For cutting purposes, the angle delta (o) between tip 1252 of cutter 1254 and inner edge 12:6 of cutter 1234 is preferably about 37 degrees.
Turning now to FIG. 39, a vertical cross-sectional view of still another embodiment of our novel disc cutter 1300 is illustrated. Here where the disc cutter 1300 now employs an outwardly facing "single" or one-half face type seal assembly 1302 with a chevron ring 1304 and o-ring 1306.
Sealing ring 1304 acts between backing ring 1308 on shaft flange 1310 and inner flange 1312 on cutter ring 1319, to absorb axial loading. Radial loading is accomodated by a journal bearing 1316. In this arrangement, I have found adequate, and the inner bearing diameter BI is about 1.181 inches (3.0 cm), and the outer bearing diameter BA is about 1.413 inches (3.59 cm). The bearing retainer diameter BR is about 1.6 inches (4.06 cm), and the hubcap diameter HC is about 1.8725 inches (4.76 cm).
FIG. 40 is a vertical cross-sectional view of still another embodiment of our novel disc cutter 1400, where the disc cutter now employs an "O-ring" 1402 seal centered between groove 1404 provided in a flange 1405 of the cutter ring 1406 and groove 1406 provided on raised portion 1408 of shaft 1410. An angled journal bearing 1420, with an inner portion 1422 and outer portion 1424, and upper poriton 1426 (may be split to 1426a and 1426b) is utilized to provide for both radial and axial loads. The journal bearing angle AB is ideally in the 140 degree range.
FIG. 41 is a side elevation view of the hubcap 1450 used on the disc cutter illustrated in the accompanying FIG.
40, showing the groove 1452 for accomodating and sealing bellows 1206.
In summary, it can be readily appreciated that our novel small diameter, minimal bearing space, and uniquely shaped cutting head disc cutter is not to be limited to a particular mounting technique, but may be employed in what may be the most advantageous mount in any particular application.
Similarly, although the research connected with the development of our novel disc cutter demonstrated the advantages of using the smallest diameter cutter possible in any given application, our novel cutter could be built in fit into existing mounts of prior art excavating equipment.
Therefore, it is to be appreciated that the disc cutter provided by the present invention is an outstanding improvement in the state of the art of drilling, tunnel boring, and excavating. Our novel disc type cutterhead which employs our novel disc cutters is relatively simple, and it substantially reduces the weight of cutterheads.
Also, our novel disc cutter substantially reduces the thrust required for drilling a desired rate, or, dramatically increases the drilling rate at a given thrust. Also, our novel disc cutter substantially reduces the costs of maintaining and rebuilding of cutterheads or bit bodies.
It is thus clear from the heretofore provided description that our novel disc cutter, and the method of mounting and using the same in a cutterhead, is a dramatic improvement in the state of the art of tunnel boring, drilling, and excavating. It will be readily apparent to the reader that the our novel disc cutter and cutterhead may be easily adapted to other embodiments incorporating the concepts taught herein and that the present figures as shown by way of example only and are not in any way a limitation.
Thus, the invention may be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The embodiments presented herein are therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalences of the claims are